Refrigerant Flow Control for an Evaporative Atmospheric Water Condenser

ABSTRACT

An atmospheric evaporative water condenser is disclosed which includes a refrigerant flow control system. The flow control system has a number of temperature sensors mounted throughout the apparatus which sends signals to a computerized controller. The computerized controller evaluates the signals from the temperature sensors which in turn opens or closes a plurality of expansion valves. This alters the flow of a refrigerant through the pipes of various portions of the apparatus, causing temperature of fins through which the pipes pass to maintain an optimal temperature for condensation. This avoids undesirable ice formation, film buildup and frost buildup on the fins. As air passes over the optimized cooled fins, water entrained in the air condenses into liquid state on the fins and is collected.

RELATED PATENT APPLICATIONS

This utility patent application claims priority from Provisional Patent Application 61/789,372 filed on Mar. 15, 2013, titled “Refrigerant Flow Control For an Evaporative Atmospheric Water Condenser”, Provisional Patent Application 61/831,231 filed on Jun. 5, 2013 titled “Refrigerant Flow Control For an Evaporative Atmospheric Water Condenser”, and Provisional Patent Application 61/788,718 filed on Mar. 15, 2013 titled “Fin Spacing on an Evaporative Atmospheric Water Condenser” all of which are incorporated herein in their entirety.

BACKGROUND OF THE INVENTION

Devices which extract water from the atmosphere employ a refrigerant pumped through a tube or coil. The tube includes a plurality of fins which are cooled through the heat transfer process. The refrigerant goes through a cycle where initially the mixture of liquid refrigerant and vapor refrigerant evaporates completely in the evaporator coil when it removes the heat out of air passing across the coils and fins; then the refrigerant is compressed in the compressor and it becomes high pressure refrigerant in gaseous form; the refrigerant is then cooled in condenser coils where it condenses into liquid refrigerant; the liquid refrigerant then flows toward the evaporator where expansion valves cause it to chill and become a cold mixture of liquid and vapor refrigerant which then re-starts the cycle. As used herein, cycle generally refers to the cycle described above.

Water condenses out of the air onto the fin surfaces and is collected for use. In the system described above, the working fluid is re-compressed and then pumped through the tube again in a continuous process. The efficiency of such refrigeration cycles employed in devices which remove water from the air is impaired when the water freezes on the fin surfaces or frost forms on the fins or too much water forms on the fins as a thick film of water. Ice, frost and thick films of water inhibit heat transfer in the same way that a layer of ice can. It is desirable to maintain an appropriate temperature on the fin surface to permit the water to condense out of the air on to the fin surface without freezing or any of the aforementioned conditions occurring.

Devices which extract water from the atmosphere employ a refrigerant pumped through a tube or coil which in turn extracts heat from a stream of air by dropping temperatures of the coils and the plurality of fins attached to these coils and the air in the proximity of these fins to below the dew point temperature of air and thus initiating condensation of the moisture in the air. The refrigerant goes through a cycle where initially the mixture of liquid refrigerant and vapor refrigerant evaporates in the evaporator coil extracting the heat out of air passing across the coils and fins; then the refrigerant is compressed in the compressor and it becomes high pressure refrigerant in gaseous form; the refrigerant is then cooled in condenser coils where it condenses into liquid refrigerant; the liquid refrigerant then flows toward the evaporator where expansion valves cause it to chill and become a cold mixture of liquid and vapor refrigerant which then re-starts the cycle. As used herein, the cycle generally refers to the aforedescribed cycle.

Water condenses out of the air onto the fin surfaces and is collected for use. In the system described above, the working fluid is re-compressed and then pumped through the tube again in a continuous process. Excessive heat removal or low air stream velocity can result in sub-cooling of coils and fins and eventual ice formation. Ice build-up makes fins ineffective by curtailing air flow and virtually ending the condensation process. On the other hand, too little heat removal or high air stream velocity lead to fin surface temperatures above the dew point temperature requirements for condensation. Since heat removal is a function of refrigerant flow and temperature, and air stream velocity is affected by overall volumetric air flow, fin spacing, fin characteristics and geometry, finding the “sweet spot” where all these design and operational factors result in the optimum overall design has been difficult.

The refrigerant pipes or coils are attached to fins that act as extended surfaces to enhance heat transfer between the refrigerant and the air flow through and across the coil-fin assembly. The geometry of the coil-fin can vary depending on physical size constraints, air volumetric flow requirements, and a number of other factors. All evaporators include a plurality of coils and plurality of fins that are designed to achieve good heat transfer and air flow characteristics. The refrigerant flow through the coils is normally set and rarely controlled based on any temperature feedback. The fin thickness and spacing are also uniform through evaporators without any consideration for the fact that the refrigerant in the coils changes temperature as its temperature rises between the inlet and the outlet as it extracts heat from the condensing air. This practice is based on traditional fabrication techniques.

Prior art involves trial and error solutions where one or two variables were optimized but not the entirety of the inter-related heat transfer, fluid flow, and thermodynamics of moist air. Thermodynamics of moist air is called psychrometrics. By treating the entire evaporator with its coils and associated fins, as well as the volumetric flow, velocity of the air stream, and the psychrometric condition of the air stream as a complete multi-input multi-output (MIMO) system, the invention described below, uses active and passive control methods to take the guesswork out of the optimization process. The simultaneous control of the heat removal through refrigerant flow control in sub-sections of the coil-fin assembly, called the evaporator, in conjunction with flow and fin spacing control and adjustment will allow optimized water removal under variable atmospheric conditions. Inefficient techniques developed to deal with operational uncertainty such as periods of allowing ice to form and then thawing will be obsolete as intelligent controllers will keep the fin surfaces ideal for condensation continuously for all sections at all times. The efficiency of such refrigeration cycles employed in devices which remove water from the air is impaired when the water freezes on the fin surfaces or frost forms on the fins or too much water forms on the fins as a thick film of water. Ice, frost and thick films of water inhibit heat transfer in the same way that a layer of ice can. It is desirable to maintain an appropriate temperature on the fin surface to permit the water to condense out of the air on to the fin surface without freezing or any of the aforementioned conditions that reduce condensation of water occurring.

BRIEF DESCRIPTION OF THE INVENTION

The terms pipes or tubes may be used interchangeably and have equivalent meanings. The invention is to control the flow of refrigerant through different regions of the path of the pipe through the fins in response to variations in temperatures measured in these reasons by thermistors or other temperature sensors. This is accomplished through the use of a microprocessor in communication with a plurality of temperature sensors affixed to various places on coiled tubes on which a plurality of fins are provided. The refrigerant flow through the coiled tubes vary the temperature of the fins through classic heat transfer processes. When the temperature of the fins is determined to be below or above a programmed range of temperatures, the microprocessor can open or close any of a plurality of computer controlled electronic expansion valves (hereafter referred to as EEV's). This would have the effect of stopping the flow of refrigerant in areas of the coiled tubes that are determined to be too cold, or increasing the flow of refrigerant in areas of the coiled tubes that are determined to be too warm. This would be accomplished by placing a manifold at the entry of the tube entering the fins. The manifold would direct refrigerant to a number of regions in the overall fin zone. Instead of a single tube entering into the fin zone, multiple tubes are provided at the exit of the manifold which enter the fin zone at multiple locations. This permits the flow of refrigerant to be modified at different areas of the fin zone. By the microprocessor selectively opening and closing the EEV's due to sensor signals monitoring the temperature in different regions of the fin zone, the flow of refrigerant to that zone may be modified, thus altering the heat transfer to the fins. Specific parameters would be set on the microprocessor to determine when the EEV's should be opened or closed to create a “sweet spot” to prevent icing of the fins in the entire fin zone. This would maximize the efficiency of the apparatus. The microprocessor may include a MIMO device, a Multi-Input, Multi-Output Controller, and the two terms may be used interchangeably. Thus, the apparatus would remove the maximum amount of water possible from a given volume of air. Apparatus power requirements would also be optimized (in the sense to use the least amount of power) to produce the greatest amount of water.

This invention optimizes the operation of water making machines by combining a passive design improvement, with an active refrigerant control system. The passive design consists of changing fin spacing by considering the fact that refrigerant temperature rises from inlet to outlet regardless of whether its flow is limited to a single tortuous pipe with attached fins or an arrangement of tortuous pipes and attached fins that may be connected in series or in parallel. The rise in the temperature of the refrigerant results in a variation in the delta T or the temperature difference between the air and the fins affixed to the pipes. The changing delta T results in uneven heat transfer and unequal condensation with some sections of the evaporator freezing and some sections too warm to induce condensation. Since the passive design is still limited in practice with only two or three variations in fin spacing in each evaporator coil, this invention incorporates the active control of refrigerant flow through different regions of the path of the coil through the evaporator. The control is implemented through a microprocessor connected to a plurality of temperature sensors affixed to various places on coiled tubes on which a plurality of fins are provided. The refrigerant flow through the coiled tubes vary the temperature of the fins through classic heat transfer processes. When the temperature of the fins is determined to be below or above a pre-programmed range of temperatures, the microprocessor can open or close any of a plurality of computer controlled electronic expansion valves This would have the effect of impeding the flow of refrigerant in areas of the coiled tubes that are determined to be too cold, or increasing the flow of refrigerant in areas of the coiled tubes that are determined to be too warm. This would be accomplished by placing a manifold at the entry of the tube entering the evaporator. The manifold would direct refrigerant to a number of regions in the evaporator. Instead of a single tube entering into the evaporator, multiple tubes are provided through a distribution manifold that directs refrigerant flow to different sections of the evaporator. By providing individual refrigerant flow paths to different areas of the evaporator, flow controllers or EEVs can be utilized to modify the volumetric delivery of refrigerant to each section of the evaporator. By the microprocessor selectively opening and closing the EEV's due to sensor signals monitoring the temperature in different regions of the fin zone, the flow of refrigerant to that zone may be modified, thus altering the heat transfer to the fins.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a first embodiment of a partial cutaway of a one column coil evaporator of a water generating apparatus showing the tortuous path of the coiled refrigerant pipes as they would pass through the fins, the three way manifold, the three EEV's located outside the fin zone, and the multiple thermistors mounted on the refrigerant pipes and fins, and the top, middle and bottom independently temperature controlled regions of the overall fin zone.

FIG. 1A is a view of a second embodiment of the coil evaporator shown without the fins.

FIG. 2 is second embodiment of a partial cutaway of a one column coil evaporator of a water generating apparatus showing the tortuous path of the refrigerant pipes as they would pass through the fins, the three way manifold, the three EEV's located outside the fin zone, and the multiple thermistors mounted on the refrigerant pipes and fins, and the top, middle and bottom independently temperature controlled regions of the overall fin zone.

FIG. 3 is a table showing the mass percent of the refrigerant that would pass through each of the three EEV's and into the fin zone of a one column coil evaporator of a water generating apparatus depending on the condition of each of the EEV's (open or closed).

FIG. 4 is a partial cutaway of a three column coil evaporator of a water generating apparatus showing the tortuous path of the refrigerant pipes as they would pass through the fins, four three way manifolds, and the nine EEV's located outside the fin zone, the multiple thermistors mounted on the refrigerant pipes and fins, and the top, middle, bottom, right, center and left regions of the fin zone, forming nine independently temperature controlled regions within the overall fin zone.

FIG. 5 is a view of the apparatus taken along line 5-5 of FIG. 4.

FIG. 6 is a view of the embodiment of the invention taken along lines 8-8 of FIG. 4.

The above brief description of the drawings will be clearly understood during the explanation of the specific elements of the apparatus of the detailed description of the drawings which follows.

DETAILED DESCRIPTION OF THE DRAWINGS

Referring to FIG. 1, a one column coil evaporator of a water generating apparatus 100 is shown. In this cut away view, the tortuous single column of coils 1 is shown in contact with a unit width of fins 2. The fins 2 in reality fill in the gap over the single column of coils 1 up to the rightmost coil 101.

The unit width of fins 2 is divided into three control areas A3, B4, and C5. Control area A3, B4, and B5 all extend to the rightmost coil 101. The three control areas A3, B4, and C5 are controlled by three (3) Electronic Control Valves (EEV's). Control area A3 is controlled by EEV 8. Control area B4 is controlled by EEV 9. Control area C5 is controlled by EEV 10. EEV 8, EEV 9, and EEV 10 are opened and closed by a microprocessor or other controller, such as a MIMO (multi-input, multi-output) controller (both not shown). The EEV 8, EEV 9, and EEV 10, regulate and measure the refrigerant flow to the three control areas A3, B4, and C5 respectively. The EEV's in FIG. 1 may be placed as shown or in another appropriate positions.

The refrigerant is pumped into the one column coil evaporator of a water generating apparatus 100 through input tube 6, where it immediately flows into a three (3) way manifold 7. When EEV 8, EEV 9, and EEV 10 are open, the refrigerant would flow equally throughout the fin zone's three control areas A3, B4, and C5 equally. A plurality of temperature sensors 14, 15, 16, 17, 18, and 19 are placed in the fin zone and/or on the coil. Temperature sensor 14 on coil 1 and temperature sensor 15 on fin 2 are in control area A3. Similarly, sensors 16 and 17 are in control area B4, and sensors 17 and 18 in control area C5. The position of the temperature sensors 14, 15, 16, 17, 18 and 19 are not limited to the positions that they are shown, but may be placed at other locations if necessitated. Further additional temperature sensors may be used. The plurality of temperature sensors 14, 15, 16, 17, 18, and 19 measure the temperature at each particular location and send a signal to the microprocessor or other controller (not shown). Based on the measured temperatures, the microprocessor or other controller would open of close EEV 8, EEV 9, or EEV 10 to adjust the flow of refrigerant through control areas A3, B4, and C5, thus altering the temperature where and when it is needed to prevent or stop ice from forming on the fins 2.

In FIG. 1 it can be seen that after the refrigerant flow exits EEV 8, it flows into a single tube 102 into the fin zone 2. After the refrigerant exits EEV 9, it enters a bifurcated tube 11 into the fin zone 2. After the refrigerant exits EEV 10 it enters a second bifurcated tube 12.

The refrigerant has three entry points into the fin zone 2 from the input tube 6: single tube 102, bifurcated tube 11 and bifurcated tube 12 when all three EEV's (EEV 8, EEV 9 and EEV 10) are open. Since some of the time the refrigerant flow may be arrested due to the fact that one or more of the EEV's may be closed due to fin temperature considerations, there will be mixing of refrigerants of different temperatures in the tortuous single column of coils 1. The refrigerant leaves the fins 2 by passing through the tortuous single column of coils where it reaches the refrigerant exit tube 13. Since this is a closed loop, the refrigerant will then be compressed in a compressor (not shown), where the refrigerant is re-cooled and then pumped by a pump (not shown) back to the input tube 6. Further the warm humid air from which the water is being removed, is forced over the fins 2 by a fan or the like. In this fashion, the temperature in the fin zone 2 is kept within a range which maximizes the efficiency of the one column coil evaporator of a water generating apparatus 100 by preventing unwanted icing of the fins 2. Means to collect the purified water (not shown) which falls due to gravity off the fins 2 are provided.

FIG. 1A shows an alternate layout of the tortuous coil or tube 1′. The fins 2 are not shown; however, when they would be installed, they would have the appearance very similar to those shown in FIG. 1 with the exception of a new pathway for the refrigerant. The refrigerant is pumped into the one column coil evaporator of a water generating apparatus 100′ through input tube 6′, where it immediately flows into a three (3) way manifold 7′. About a third of the refrigerant flows to EEV 8′ which when open permits the refrigerant to flow into the top tube 102′ of the tortuous tube. It can be seen that the refrigerant in this embodiment which enters tube 102′ reaches a leftmost portion of tube 11′ where the refrigerant is shunted and flows into vertical tube 103 and flows downward until it reaches the refrigerant exit tube 13′. About another third of the refrigerant flows from the three way manifold 7′ to EEV 9′ which enters tube 104′ till it flows past the leftmost portion of the tube 12′ where the refrigerant is shunted and flows into vertical tube 103 and flows downward until it reaches the refrigerant exit tube 13′. About another third of the refrigerant flows from the three way manifold 7′ to EEV 10′ which enters tube 105′ until it reaches the bottom most tube 1′ of the tortuous tube where it merges with vertical tube 103 and the last third of the refrigerant exits tube 13′ with the first two thirds of the refrigerant to further flow to a compressor which compresses the now vaporous refrigerant back to an about an ambient temperature refrigerant fluid which is expanded and cooled passing through the EEV's and the cycle continues. If fins were shown in this FIG. 1A, humidity in the air would condense on the fins and the water would be collected.

Referring to FIG. 2, a one column coil evaporator of a water generating apparatus 100′ with fins 2′ is shown. In this cut away view, the tortuous single column of coils 1′ is shown in contact with a unit width of fins 2′. The fins 2′ fill in the gap over the single column of coils 1′ up to the rightmost fin 201′.

The unit width of fins 2′ is divided into three control areas A3′, B4′, and C5′. The three control areas A3′, B4′, and C5′ are controlled by three (3) Electronic Control Valves (EEV's). Control area A3′ is controlled by EEV 8′. Control area B4″ is controlled by EEV 9′. Control area C5′ is controlled by EEV 10′. EEV 8, EEV 9, and EEV 10 are opened and closed by a microprocessor or other controller (not shown). The EEV 8′, EEV 9′, and EEV 10′, regulate and measure the refrigerant flow to the three control areas A3′, B4′, and C5′ respectively. The EEV's in FIG. 2 may be placed as shown or in another appropriate position.

As shown in FIG. 2, the refrigerant is pumped into the one column coil evaporator of a water generating apparatus 100′ through input tube 6′, where it immediately flows into a three (3) way manifold 7′. When EEV 8′, EEV 9′, and EEV 10′ are open, the refrigerant would flow equally throughout the fin zone's three control areas A3′, B4′, and C5′ equally. A plurality of temperature sensors 14′, 15′, 16′, 17′, 18′, and 19′ are placed in the fin zone, and as described in the embodiment in FIG. 1, temperature sensors 14′ and 15′ control area A3′, 16′ and 17′ control area B4′, and 17′ and 18′ control area C5′. The position of the temperature sensors 14′, 15′, 16′, 17′, 18′ and 19′ are not limited to the positions that they are shown, but may be placed at other locations if necessitated. The temperature sensors 14′, 15′, 16′, 17′, 18′ and 19′ measures the temperature at their particular location and sends a signal to the microprocessor or other controller (not shown). Based on the measured temperatures, the microprocessor or other controller would open of close EEV A3′, EEV B4′, or EEV C5′ to adjust the flow of refrigerant through control areas A3′, B4′, and C5′, thus altering the temperature where and when needed to prevent or stop ice from forming on the fins 2′.

The refrigerant has three entry points due to the three way manifold 7′ prior to the fin zone from the input tube 6′: single tube 102′ exiting EEV 8′, the single tube 104′ exiting EEV 9′, and a single tube 105′ exiting after EEV 10′ when all EEV's (EEV 8′, EEV 9′ and EEV 10′) are open. In some future embodiments of the Refrigerant Flow Control for an Atmospheric Water Condenser, some of the time the refrigerant flow may be arrested due to the fact that one or more of the EEV's may be closed due to temperature considerations. In this embodiment, refrigerant entering tube 102′ when EEV 8′ is opened will cascade through the tube pathway in fin area A3′ until it meets shunt tube 86 which is connected to vertical tube 103′ permitting the refrigerant entering from EEV 8′ to enter tube 103′ where it will flow directly to the refrigerant exit tube 13. This allows the refrigerant from control area A3′ not to mix with the refrigerants from control areas B4′ and C5′. In addition, the refrigerant which enters EEV 9′ when it is open will cascade through the tube pathway in fin area B4′ until it meets shunt tube 86′ which is connected to vertical tube 103′ permitting the refrigerant entering from EEV 9′ to enter tube 103′ where it will flow directly to the refrigerant exit tube 13. where it also enters tube 103′ where it will flow downward directly to the refrigerant exit tube 13′. The portion of the refrigerant entering EEV 10′ from the manifold 7′ passes through the tube pathway in fin area C5′ where it mates up with the first two refrigerant flows from fin region A3′ and B4′ which flows down vertical tube 103′ which is connected refrigerant exit tube 13′. Since the refrigerant flowing from EEV 10′ exits directly to refrigerant exit tube 13′ there is no requirement for a shunt tube. This allows for simpler control, since the number of temperature variables are reduced.

Since this is a closed loop, the refrigerant will then be compressed in a compressor (not shown) and flows back to the input tube 6′. Further the warm humid air from which the water is being removed, is forced over the fins by a fan or the like. In this fashion, the temperature in the fin zone is kept within a range which maximizes the efficiency of the one column coil evaporator of a water generating apparatus 100′ by preventing unwanted icing of the fins 2′. Means to collect the condensed purified water (not shown) which falls due to gravity off the fins 2′ are provided.

Referring to FIG. 3, a logic table is presented showing the mass fraction of refrigerant flow in both embodiments of a one column coil evaporator of a water generating apparatus 100 or 100′ with the three EEV's (8′,9′,10′) or (8,9,10) in open and closed positions. Both embodiments shown would have the same mass fraction since tube 103 in the second embodiment would not affect the refrigerant which exits the manifold 7. In the case in which EEV's 8, 9, and 10 were instructed to be all open, control sections 3A, 4B, and 5C would receive thirty three percent (33%) of the refrigerant after exiting the manifold 7. If EEV 9 were closed then EEV 8 and EEV 9 would each receive a fifty percent (50%) mass fraction of refrigerant. One can easily see the effect of the opening and closing of the EEV's would have on the control sections to which they exit into.

Just as in the simpler embodiment shown in FIG. 2, where the refrigerant enters a single manifold into 1 tortuous tube path, the embodiment of FIG. 4 shows three of these manifold in side by side relation, each connection to 3 EEV's and to three columns of tortuous tubes. Referring to FIG. 4 an alternate embodiment shows a three column coil evaporator of a water generating apparatus 200 is shown. In this cut away view, the tortuous three columns of coils 1″ is shown in contact with a unit width of fins 2″. The fins 2″ in reality fill in the gap over the three columns of coils 1″ up to the rightmost fin 101″.

The unit width of fins 2″ is divided into nine control areas. The topmost three (3) control areas B1, B2 and B3 extend down the top third A3″ of the unit width of fins 2″. The middle three (3) control areas B1, B2 and B3 extend downward to the middle third of the unit width B4″ of the fins 2″. The bottom three (3) control areas C1, C2 and C3 extend downward to the bottom third of unit width of the fins 2″. The middle third control areas and the bottom third control areas are not shown in this figure, however they mimic the top control areas A1, A2 and A3 in every way except position.

The top control areas A1, A2 and A3 are provided refrigerant by the state of the three (3) EEV's (8,1), (8,2) and (8,3). If any of three (3) EEV's (8,1), (8,2) and (8,3) are open, refrigerant flows, if closed, no refrigerant flows to those upper control areas.

The middle control areas B1, B2 and B3 are provided refrigerant by the state of the three (3) EEV's (9,1), (9,2) and (9,3). If any of three (3) EEV's (9,1), (9,2) and (9,3) are open, refrigerant flows, if closed, no refrigerant flows to those middle control areas.

The bottom control areas C1, C2 and C3 are provided refrigerant by the state of the three (3) EEV's (10,1), (10,2) and (10,3). If any of three (3) EEV's (10,1), (10,2) and (10,3) are open, refrigerant flows, if closed, no refrigerant flows to those bottom control areas.

In the embodiment of FIG. 4, the refrigerant which enters tubes in (A3′, B1), (A3′, B2) and (A3′, B3) from EEV (8,1), EEV (8,2) and EEV 8,3) all exit into three parallel downward pipes 103″ where the refrigerant, after cascading through the pipes of the A3′ fin section, each intersect with the three refrigerant exit tubes 130.

EEV's (8,1), (8,2), (8,3), (9,1), (9,2), (9,3), (10,1), (10,2) and (10,3) are opened and closed by a microprocessor or other controller (not shown). EEV's (8,1), (8,2), (8,3), (9,1), (9,2), (9,3), (10,1), (10,2) and (10,3) regulate and measure the refrigerant flow to the nine control areas A1, A2, A3, B1, B2, B3, C1, C2 and C3 respectively.

The EEV's in FIG. 4 may be placed as shown or in another appropriate position.

The refrigerant flows into the three column coil evaporator of a water generating apparatus 200 through refrigerant input tube 60, where it immediately flows into a first three (3) way manifold 23. The refrigerant flow is then sent to a second three (3) way manifold 20, a third three (3) way manifold 21 and a fourth three (3) way manifold 22. 100% of the mass fraction of the refrigerant enters the first three (3) way manifold 23. 33% of the mass fraction of the refrigerant enters the second three (3) way manifold 20, the third three (3) way manifold 21 and the fourth three (3) way manifold 22 respectively. 11% of the refrigerant mass can enter or exit each one of the EEV's (8,1), (8,2), (8,3), (9,1), (9,2), (9,3), (10,1), (10,2) and (10,3) depending if they are opened or closed.

Although not shown in FIG. 4, Eighteen (18) temperature sensors are distributed throughout the nine control areas A1, A2, A3, B1, B2, B3, C1, C2 and C3. Their arrangement may be similar to that of the temperature sensors shown in the one column coil evaporator 100 or in another configuration.

By monitoring the temperature of the fins and tubes in the nine control areas A1, A2, A3, B1, B2, B3, C1, C2 and C3, the microprocessor can determine whether to open or close any one, more than one, or all of the EEV's (8,1), (8,2), (8,3), (9,1), (9,2), (9,3), (10,1), (10,2) and (10,3) and maintain a temperature in the fin region 2″ of the three column coil evaporator of a water generating apparatus 200. This would prevent unwanted icing along any of the fins therein, thus maintaining a higher efficiency of water production than when such fins have iced up. The present invitation provides for control of fins within fin region 2″ to prevent or minimize icing in specific areas while maintaining the efficiency of the conversion of and manufacture of water.

As discussed the refrigerant has nine entry points into the fin zone from the input tube 60 (after passing through the four three (3) way manifolds, 20, 21, 22 and 23. In this embodiment even with all of the opening and closing of EEV's there will be little mixing of refrigerant throughout the nine control areas A1, A2, A3, B1, B2, B3, C1, C2 and C3.

Being a closed system, after passing through the tortuous three columns of tubes, the refrigerant would exit by the three exit tubes 130. Another three way manifold 130 A, would combine the flow of refrigerant in tube 130B back to the 100% mark.

Again this is a closed loop, between the inlet tube 60 and the output tube 130B. After exiting the output tube 130A After the refrigerant exits the evaporator coil, it has basically vaporized by absorbing the heat from the air through the coils and the fins. The refrigerant in the vapor form is then sucked in to the low pressure side of a compressor (not shown). The refrigerant is superheated so that no refrigerant in the form of liquid enters the compressor as this could lead to compressor damage. The refrigerant is then compressed to a high pressure and very hot gas in the compressor. The hot as is then forced out of the outlet of the compressor into the condenser coils where it is cooled and condensed to a liquid form. The refrigerant which is now at ambient air temperature is fed through a metering device and a thermal expansion valve (or in our case distributed set of controlled EEVs) where it is cooled through the expansion process. It then enters the evaporator and the cycle is repeated. A pump or other mechanism to move the refrigerant to or from the compressor may be employed.

In use, warm humid air from which the water is being removed is forced over the fins 2″ by a fan or the like. By automatic computer control techniques, the EEV's are opened and closed response to the multiple temperature sensor inputs into the computer or microprocessor. This computer has a algorithm which causes the EEVs to open or close thus altering the flow of the refrigerant independently through any or all of the 9 of tortuous tubing 1″ and fins 2″. By the constantly varying of heat transfer between the fins 2″ and the tortuous tubes 1″ a range of temperatures may be maintained in the fins zone. In this fashion, the temperature in the fin zone 2″ is kept within a range which maximizes the efficiency of the three column coil evaporator of a water generating apparatus 200 by preventing unwanted icing of the fins 2″. This can be done in any one of the nine (9) zones shown and more or less zones can be incorporated within the scope of the present invention with more or less, a plurality EEVs and temperature sensors.

A manifold system including a single refrigerant input 60 into a first three way manifold 23, where each of the three refrigerant outputs from the first three way manifold 23 enter a second three way manifold 20, a third three way manifold 21 and a fourth three way manifold 22, form nine refrigerant outputs which enter the apparatus 200 as shown in FIG. 4.

FIG. 5 is a view of the apparatus 200 taken along line 5-5 of FIG. 4. The top manifold 23 is shown with the refrigerant entry tube 60. The bottom manifold 130A is shown with the refrigerant exit tube 130B. Downward tubing 103 is shown which brings refrigerant from the upper portions of the apparatus 200 to the bottom manifold 130A. The refrigerant then exits through tube 130B.

After the refrigerant (working fluid) exits tube 130B, it has basically been substantially vaporized by absorbing the heat from the air through the coils and the fins. The refrigerant in the vapor form is then sucked in to the low pressure side of a compressor (not shown). The refrigerant is superheated so that no refrigerant in the form of liquid enters the compressor as this could lead to compressor damage. The refrigerant is then compressed to a high pressure and very hot gas in the compressor. The hot gas is then forced out of the outlet of the compressor into the condenser coils where it is cooled and condensed to a liquid form. The refrigerant which is now at ambient air temperature is fed through a metering device and a thermal expansion valve (or in our case distributed set of controlled EEVs) there it is cooled through the expansion process and the cycle is repeated.

FIG. 6 shows a view of the atmospheric water condenser 200 taken along line 8-8 of FIG. 4 which shows the area behind the manifolds 23 and 130A.

The fin structure 101″ has a plurality of serpentine or tortuous pipes 1″ or tubes 1″ running through three vertical sections of the fins 2″. The three top manifolds 20″, 21″, and 22″ separate the incoming refrigerant into 9 pipe sections, which each intersect a computer controlled EEV. EEV's (8,1); (8,2); and (8,3) are occluded by three top manifolds 20, 21, and 22 (they are best seen in FIG. 4); permits refrigerant to flow or not to flow depending on the computer analysis of the temperatures of the right side B1 of the upper portion A3″, the middle side B2 of the upper portion A3″, and the left side of B3 of the upper portion A3″. Approximately ⅓ the way down the atmospheric water condenser 200, on each section of pipe which is affixed to EEV's (8,1); (8,2); and (8,3), a vertical linear exit pipe 103″ is connected to the serpentine pipe 1″ at point 85. When the refrigerant is flowing and reaches point 85 it is shunted into it's respective vertical exit pipe 103″ and the refrigerant flows down into it's respective one of the three refrigerant exit pipes 130. Although this point is proximal EEV's (9,1); (9,2); and (9,3) the vertical linear exit pipe 103 there is no proximal connection with the pipes associated with (9,1); (9,2); and (9,3).

EEV's (9,1); (9,2); and (9,3); permits refrigerant to flow or not to flow depending on the computer analysis of the temperatures of the right side B1 of the middle portion B4″, the middle side B2 of the middle portion B4″, and the left side of B3 of the middle portion B4″. Approximately ⅔ the way down the atmospheric water condenser 200, on each section of pipe which is affixed to EEV's (9,1); (9,2); and (9,3), the vertical linear exit pipe 103″ again connected to the serpentine pipe 1″ at point 85′. When the refrigerant is flowing and reaches point 85′ it is shunted into it's respective vertical exit pipe 103″ where the refrigerant flows down into it's respective one of the three refrigerant exit pipes 130. Although this point is proximal EEV's (10,1); (10,2); and (10,3) the vertical linear exit pipe 103″ there is no proximal connection with the pipes associated with (10,1); (10,2); and (10,3).

EEV's (10,1); (10,2); and (10,3); permits the refrigerant to flow or not to flow depending on the computer analysis of the temperatures of the right side B1 of the bottom portion C5″, of the middle side B2 of the bottom portion C5″, and of the left side of B3 of the bottom portion C5″.

When the refrigerant is flowing and reaches point 85″ it is shunted directly into it's respective one of the three refrigerant exit pipes 130.

As best seen in FIG. 4, the three refrigerant exit pipes 130 enter exit manifold 130A and exit into the refrigerant exit tube 130B.

After the refrigerant (working fluid) exits tube 130B, it has basically been substantially vaporized by absorbing the heat from the air through the coils and the fins. The refrigerant in the vapor form is then sucked in to the low pressure side of a compressor (not shown). The refrigerant is superheated so that no refrigerant in the form of liquid enters the compressor as this could lead to compressor damage. The refrigerant is then compressed to a high pressure and very hot gas in the compressor. The hot gas is then forced out of the outlet of the compressor into the condenser coils where it is cooled and condensed to a liquid form. The refrigerant which is now at ambient air temperature is fed through a metering device and a thermal expansion valve (or in our case distributed set of controlled EEVs) where it is cooled through the expansion process and the cycle is repeated.

One form of the invention comprises a refrigerant flow control apparatus for an evaporative atmospheric water condenser which includes a refrigerant, a first electronic expansion valve connected to a first portion of serpentine pipe, a second electronic expansion valve connected to a second portion of serpentine pipe, a third electronic expansion valve connected to a third portion of serpentine pipe, a plurality of vertically disposed parallel condensation fins each fin having a height, a width and a thickness, the plurality of fins having a length, the length extending from a leftmost fin to a rightmost fin, each fin having an upper zone, a middle zone and a bottom zone,

the first portion of serpentine pipe passes perpendicularly and centrally through the fins and along the length of the plurality of fins from about a top of the fins to about ⅓ down height of the fins, and the second portion of serpentine pipe passing perpendicularly and centrally through the fins and along length of the plurality of fins from about ⅓ down the height of the fins to about ⅔ down the height of the fins, the third portion of serpentine pipe passing perpendicularly and centrally through the fins and along the length of the plurality of fins from about ⅔ down the height of the fins to about a bottom of height of the fins, a first plurality of temperature sensors placed on the first portion of serpentine pipe, the second portion of serpentine pipe and the third portion of serpentine pipe, a second plurality of temperature sensors placed on the plurality of vertically disposed parallel condensation fins, an equal number of the temperature sensors placed along the length of the upper zone, the length of the middle zone and the length of the bottom zone, a programmable computer in communication with the first electronic expansion valve, the second electronic expansion valve and the third electronic expansion valve, the programmable computer also in communication with the first plurality of temperature sensors and the second plurality of temperature sensors, the programmable computer having a preset temperature range for each location of each one of the first plurality of temperature sensors and for each location of each one of the second plurality of temperature sensors, and the programmable computer having the capability to open or close the first electronic expansion valve, the second electronic expansion valve and the third electronic expansion valve to allow said refrigerant to flow or not to flow through said first portion of serpentine pipes, said second portion of serpentine pipes and the third portion of serpentine pipes in order to keep the temperature at each one of the first plurality of temperature sensors and at each location of the each one of the second plurality of temperature sensors within the preset range, so that water which condensates on the plurality of vertically disposed parallel condensation fins may be maximized for collection. This may be considered a single module embodiment, since there is only one closed refrigerant tube winding in a serpentine path through the fins cooling them to allow moisture to condense thereon.

Another form of the invention contemplates the use of three modules, where the module may be likened to a manifold for distributing the refrigerant in three refrigerant serpentine tube windings which are both initially distributed to the modules by a manifold and returned to a single exit flow prior to the compressor by a manifold.

Such a embodiment of the invention would be a refrigerant flow control apparatus for an evaporative atmospheric water condenser which includes a refrigerant including a first module including a first electronic expansion valve connected to a first portion of serpentine pipe, a second electronic expansion valve connected to a second portion of serpentine pipe, a third electronic expansion valve connected to a third portion of serpentine pipe, a second module including a fourth electronic expansion valve connected to a fourth portion of serpentine pipe, a fifth electronic expansion valve connected to a fifth portion of serpentine pipe, a sixth electronic expansion valve connected to a sixth portion of serpentine pipe, a third module including a seventh electronic expansion valve connected to a seventh portion of serpentine pipe, an eighth electronic expansion valve connected to an eighth portion of serpentine pipe, a ninth electronic expansion valve connected to a ninth portion of serpentine pipe, a plurality of vertically disposed parallel condensation fins each the fin having a height, a width and a thickness, the plurality of fins having a length extending from a leftmost fin to a rightmost fin, each the fin having an upper zone, a middle zone and a bottom zone, the first portion of serpentine pipe passing perpendicularly through the fins and along the length of the plurality of fins from about a top of the fins to about ⅓ down the height of the fins, the second portion of serpentine pipe passing perpendicularly through the fins and along the length of the plurality of fins from about the ⅓ down the height of the fins to about ⅔ down the height of the fins, the third portion of serpentine pipe passing perpendicularly through the fins and along the length of the plurality of fins from about the ⅔ down the height of the fins to about a bottom of the height of the fins, the fourth portion of serpentine pipe passing perpendicularly through the fins and along the length of the plurality of fins from about a top of the fins to about ⅓ down the height of the fins, the fifth portion of serpentine pipe passing perpendicularly through the fins and along the length of the plurality of fins from about the ⅓ down the height of the fins to about ⅔ down the height of the fins, the sixth portion of serpentine pipe passing perpendicularly through the fins and along the length of the plurality of fins from about the ⅔ down the height of the fins to about a bottom of the height of the fins, the seventh portion of serpentine pipe passing perpendicularly through the fins and along the length of the plurality of fins from about a top of the fins to about ⅓ down the height of the fins, the eighth portion of serpentine pipe passing perpendicularly through the fins and along the length of the plurality of fins from about the ⅓ down the height of the fins to about ⅔ down the height of the fins, the ninth portion of serpentine pipe passing perpendicularly through the fins and along the length of the plurality of fins from about the ⅔ down the height of the fins to about a bottom of the height of the fins, the first module, the second module and the third module are all in vertical parallel relation, a first plurality of temperature sensors placed on the first portion of serpentine pipes, the second portion of serpentine pipes and the third portion of serpentine pipes, the fourth portion of serpentine pipes, the fifth portion of serpentine pipes, the sixth portion of serpentine pipes, the seventh portion of serpentine pipes, the eighth portion of serpentine pipes, and the ninth portion of serpentine pipes, a second plurality of temperature sensors placed on the plurality of vertically disposed parallel condensation fins intermediate the first module and the second module, and the second module and the third module, an equal number of the temperature sensors placed along the length of the upper zone, the length of the middle zone and the length of the bottom zone, a programmable computer in communication with the first electronic expansion valve, the second electronic expansion valve and the third electronic expansion valve, the fourth electronic expansion valve, the fifth electronic expansion valve, the seventh electronic expansion zone, the eighth electronic expansion valve and the ninth electronic expansion valve, the programmable computer also in communication with the first plurality of temperature sensors and the second plurality of temperature sensors, the programmable computer having a preset temperature range for each location of each one of the first plurality of temperature sensors and for each location of each one of the second plurality of temperature sensors, the programmable computer having the capability to open or close the first electronic expansion valve, the second electronic expansion valve and the third electronic expansion valve, the fourth electronic expansion valve, the fifth electronic expansion valve, the seventh electronic expansion zone, the eighth electronic expansion valve and the ninth electronic expansion valve, to allow the refrigerant to flow or not to flow through the first portion of serpentine pipes, the second portion of serpentine pipes and the third portion of serpentine pipes, the fourth portion of serpentine pipes, the fifth portion of serpentine pipes, the sixth portion of serpentine pipes, the seventh portion of serpentine pipes, the eighth portion of serpentine pipes, and the ninth portion of serpentine pipes in order to keep the temperature at each location of the each one of the first plurality of temperature sensors and at each location of the each one of the second plurality of temperature sensors within the preset range, whereby condensation on the plurality of vertically disposed parallel condensation fins may be maximized for collection.

Such a refrigerant flow control apparatus for an evaporative atmospheric water condenser may be usefully employed with a fin spacing device and method which is described in Provisional Patent Application 61/788,718 filed on Mar. 15, 2013 titled “Fin Spacing on an Evaporative Atmospheric Water Condenser”, by the same inventor and which will be converted to an utility application.

Alternate methods where the refrigerant is mixed as it passes through the atmospheric water condenser have been contemplated and one possible configuration is shown in FIG. 1.

While the invention has been described in its preferred form or embodiment with some degree of particularity, it is understood that this description has been given only by way of example and that numerous changes in the details of construction, fabrication, and use, including the combination and arrangement of parts, may be made without departing from the spirit and scope of the invention. 

I claim:
 1. A refrigerant flow control apparatus for an evaporative atmospheric water condenser comprising, a refrigerant, a first electronic expansion valve connected to a first portion of serpentine pipe, a second electronic expansion valve connected to a second portion of serpentine pipe, a third electronic expansion valve connected to a third portion of serpentine pipe, a plurality of vertically disposed parallel condensation fins each said fin having a height, a width and a thickness, said plurality of fins having a length extending from a leftmost fin to a rightmost fin, each said fin having an upper zone, a middle zone and a bottom zone, said first portion of serpentine pipe passing perpendicularly and centrally through said fins and along said length of said plurality of fins from about a top of said fins to about ⅓ down said height of said fins, said second portion of serpentine pipe passing perpendicularly and centrally through said fins and along said length of said plurality of fins from about said ⅓ down said height of said fins to about ⅔ down said height of said fins, said third portion of serpentine pipe passing perpendicularly and centrally through said fins and along said length of said plurality of fins from about said ⅔ down said height of said fins to about a bottom of said height of said fins, a first plurality of temperature sensors placed on said first portion of serpentine pipe, said second portion of serpentine pipe and said third portion of serpentine pipe, a second plurality of temperature sensors placed on said plurality of vertically disposed parallel condensation fins, an equal number of said temperature sensors placed along said length of said upper zone, said length of said middle zone and said length of said bottom zone, a programmable computer in communication with said first electronic expansion valve, said second electronic expansion valve and said third electronic expansion valve, said programmable computer also in communication with said first plurality of temperature sensors and said second plurality of temperature sensors, said programmable computer having a preset temperature range for each location of each one of said first plurality of temperature sensors and for each location of each one of said second plurality of temperature sensors, said programmable computer having the capability to open or close said first electronic expansion valve, said second electronic expansion valve and said third electronic expansion valve to allow said refrigerant to flow or not to flow through said first portion of serpentine pipes, said second portion of serpentine pipes and said third portion of serpentine pipes in order to keep the temperature at each location of said each one of said first plurality of temperature sensors and at each location of said each one of said second plurality of temperature sensors within said preset range, whereby condensation on said plurality of vertically disposed parallel condensation fins may be maximized for collection.
 2. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 1 including a refrigerant input pipe connected to a manifold having a first manifold exit, a second manifold exit and a third manifold exit, said first manifold exit connected by a first pipe to said first electronic expansion valve, said second manifold exit connected by a second pipe to said second electronic expansion valve, and said third manifold exit connected by a third pipe to said third electronic expansion valve.
 3. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 2 wherein said first portion of serpentine pipe has a first refrigerant exit pipe connected to a first vertically oriented pipe, said first refrigerant exit pipe is connected to said first vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about ⅓ the height of said rightmost fin from said top of said fins, wherein all of said refrigerant which enters said first portion of serpentine pipe exits into said first vertically oriented pipe.
 4. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 3 wherein said second portion of serpentine pipe has a second refrigerant exit pipe connected to said first vertically oriented pipe, said second refrigerant exit pipe is connected to said first vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about ⅔ the height of said rightmost fin from said top of said fins, wherein all of said refrigerant which enters said second portion of serpentine pipe exits into said first vertically oriented pipe.
 5. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 4 wherein said third portion of serpentine pipe has a third refrigerant exit pipe, wherein all the refrigerant which enter said third portion of said serpentine pipe exits through said third refrigerant exit pipe, said first vertically oriented pipe connects to said third refrigerant exit pipe, said first vertically oriented pipe connects to said third refrigerant exit pipe outside of said length of fins and to the right of said rightmost fin at about said bottom of said fins, wherein all the refrigerant from said first portion of serpentine pipe, said second portion of serpentine pipe and said third portion of serpentine pipe exits through said third refrigerant exit pipe.
 6. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 5 wherein said refrigerant which exits through said third refrigerant exit pipe flows to a compressor, which compresses said refrigerant, exiting the compressor by a compressor pipe.
 7. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 6 including a pump connected to said compressor pipe to cause said refrigerant to flow into said refrigerant input pipe where said refrigerant continues to flow through said manifold into said first pipe, said second pipe and said third pipe, and further flows to said first electronic expansion valve, said second electronic expansion valve and said third electronic expansion valve respectfully, where the refrigerant is cooled by rapid expansion in each of said first electronic expansion valve, said second electronic expansion valve and said third electronic expansion valve.
 8. A refrigerant flow control apparatus for an evaporative atmospheric water condenser comprising, a refrigerant, a first module including a first electronic expansion valve connected to a first portion of serpentine pipe, a second electronic expansion valve connected to a second portion of serpentine pipe, a third electronic expansion valve connected to a third portion of serpentine pipe, a second module including a fourth electronic expansion valve connected to a fourth portion of serpentine pipe, a fifth electronic expansion valve connected to a fifth portion of serpentine pipe, a sixth electronic expansion valve connected to a sixth portion of serpentine pipe, a third module including a seventh electronic expansion valve connected to a seventh portion of serpentine pipe, an eighth electronic expansion valve connected to an eighth portion of serpentine pipe, a ninth electronic expansion valve connected to a ninth portion of serpentine pipe, a plurality of vertically disposed parallel condensation fins each said fin having a height, a width and a thickness, said plurality of fins having a length extending from a leftmost fin to a rightmost fin, each said fin having an upper zone, a middle zone and a bottom zone, said first portion of serpentine pipe passing perpendicularly through said fins and along said length of said plurality of fins from about a top of said fins to about ⅓ down said height of said fins, said second portion of serpentine pipe passing perpendicularly through said fins and along said length of said plurality of fins from about said ⅓ down said height of said fins to about ⅔ down said height of said fins, said third portion of serpentine pipe passing perpendicularly through said fins and along said length of said plurality of fins from about said ⅔ down said height of said fins to about a bottom of said height of said fins, said fourth portion of serpentine pipe passing perpendicularly through said fins and along said length of said plurality of fins from about a top of said fins to about ⅓ down said height of said fins, said fifth portion of serpentine pipe passing perpendicularly through said fins and along said length of said plurality of fins from about said ⅓ down said height of said fins to about ⅔ down said height of said fins, said sixth portion of serpentine pipe passing perpendicularly through said fins and along said length of said plurality of fins from about said ⅔ down said height of said fins to about a bottom of said height of said fins, said seventh portion of serpentine pipe passing perpendicularly through said fins and along said length of said plurality of fins from about a top of said fins to about ⅓ down said height of said fins, said eighth portion of serpentine pipe passing perpendicularly through said fins and along said length of said plurality of fins from about said ⅓ down said height of said fins to about ⅔ down said height of said fins, said ninth portion of serpentine pipe passing perpendicularly through said fins and along said length of said plurality of fins from about said ⅔ down said height of said fins to about a bottom of said height of said fins, said first module, said second module and said third module are all in vertical parallel relation, a first plurality of temperature sensors placed on said first portion of serpentine pipes, said second portion of serpentine pipes and said third portion of serpentine pipes, said fourth portion of serpentine pipes, said fifth portion of serpentine pipes, said sixth portion of serpentine pipes, said seventh portion of serpentine pipes, said eighth portion of serpentine pipes, and said ninth portion of serpentine pipes, a second plurality of temperature sensors placed on said plurality of vertically disposed parallel condensation fins intermediate said first module and said second module, and said second module and said third module, an equal number of said temperature sensors placed along said length of said upper zone, said length of said middle zone and said length of said bottom zone, a programmable computer in communication with said first electronic expansion valve, said second electronic expansion valve and said third electronic expansion valve, said fourth electronic expansion valve, said fifth electronic expansion valve, said seventh electronic expansion zone, said eighth electronic expansion valve and said ninth electronic expansion valve, said programmable computer also in communication with said first plurality of temperature sensors and said second plurality of temperature sensors, said programmable computer having a preset temperature range for each location of each one of said first plurality of temperature sensors and for each location of each one of said second plurality of temperature sensors, said programmable computer having the capability to open or close said first electronic expansion valve, said second electronic expansion valve and said third electronic expansion valve, said fourth electronic expansion valve, said fifth electronic expansion valve, said seventh electronic expansion zone, said eighth electronic expansion valve and said ninth electronic expansion valve, to allow said refrigerant to flow or not to flow through said first portion of serpentine pipes, said second portion of serpentine pipes and said third portion of serpentine pipes, said fourth portion of serpentine pipes, said fifth portion of serpentine pipes, said sixth portion of serpentine pipes, said seventh portion of serpentine pipes, said eighth portion of serpentine pipes, and said ninth portion of serpentine pipes in order to keep the temperature at each location of said each one of said first plurality of temperature sensors and at each location of said each one of said second plurality of temperature sensors within said preset range, whereby condensation on said plurality of vertically disposed parallel condensation fins may be maximized for collection.
 9. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 8 including a refrigerant input pipe connected to first manifold having a first manifold exit, a second manifold exit and a third manifold exit, said first manifold exit connected by a first pipe to a second manifold, said second manifold exit connected by a second pipe to a third manifold, said third manifold exit connected by a third pipe to a fourth manifold, said second manifold having a fourth manifold exit, a fifth manifold exit and a sixth manifold exit, said third manifold having a seventh manifold exit, an eighth manifold exit, and a ninth manifold exit, said fourth manifold having a tenth manifold exit, an eleventh manifold exit, and a twelfth manifold exit, said fourth manifold exit connected by a fourth pipe to a first electronic expansion valve, said fifth manifold exit connected by a fifth pipe to a second electronic expansion valve, said sixth manifold exit connected by a sixth pipe to a third electronic expansion valve, said seventh manifold exit connected by a seventh pipe to a fourth electrical expansion valve, said eighth manifold exit connected by an eighth pipe to a fifth electrical expansion valve, said ninth manifold exit connected by a ninth pipe to a sixth electrical expansion valve, said tenth manifold exit connected by a tenth pipe to an seventh electrical expansion valve, said eleventh manifold exit connected by an eleventh pipe to an eighth electrical expansion valve, said twelfth manifold exit connected by a twelfth pipe to a ninth electrical expansion valve.
 10. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 9 wherein said first module's said first portion of serpentine pipe has a first refrigerant exit pipe connected to a first vertically oriented pipe, said first refrigerant exit pipe is connected to said first vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about ⅓ the height of said rightmost fin from said top of said fins, wherein all of said refrigerant which enters said first portion of serpentine pipe exits into said first vertically oriented pipe; and said second module's said fourth portion of serpentine pipe has a fourth refrigerant exit pipe connected to a second vertically oriented pipe, said fourth refrigerant exit pipe is connected to said second vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about ⅓ the height of said rightmost fin from said top of said fins, wherein all of said refrigerant which enters said fourth portion of serpentine pipe exits into said second vertically oriented pipe; and said third module's said seventh portion of serpentine pipe has a seventh refrigerant exit pipe connected to a third vertically oriented pipe, said seventh refrigerant exit pipe is connected to said third vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about ⅓ the height of said rightmost fin from said top of said fins, wherein all of said refrigerant which enters said seventh portion of serpentine pipe exits into said third vertically oriented pipe.
 11. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 10 wherein said first module's said second portion of serpentine pipe has a second refrigerant exit pipe connected to said first vertically oriented pipe, said second refrigerant exit pipe is connected to said first vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about ⅔ the height of said rightmost fin from said top of said fins, wherein all of said refrigerant which enters said second portion of serpentine pipe exits into said first vertically oriented pipe; and said second module's said fifth portion of serpentine pipe has a fifth refrigerant exit pipe connected to said second vertically oriented pipe, said fifth refrigerant exit pipe is connected to said second vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about ⅔ the height of said rightmost fin from said top of said fins, wherein all of said refrigerant which enters said fifth portion of serpentine pipe exits into said second vertically oriented pipe; and said third module's said eighth portion of serpentine pipe has an eighth refrigerant exit pipe connected to a third vertically oriented pipe, said eighth refrigerant exit pipe is connected to said third vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about ⅔ the height of said rightmost fin from said top of said fins, wherein all of said refrigerant which enters said eighth portion of serpentine pipe exits into said third vertically oriented pipe.
 12. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 11 wherein said first module's said third portion of serpentine pipe has a third primary exit pipe connected to said first vertically oriented pipe, said third primary exit pipe is connected to said first vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about at about said bottom of said fins, wherein all said refrigerant from said first portion of serpentine pipe, said second portion of serpentine pipe and said third portion of serpentine pipe exits through said third primary exit pipe, and said second module's said sixth portion of serpentine pipe has a sixth primary exit pipe connected to said second vertically oriented pipe, said sixth primary exit pipe is connected to said second vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about at about said bottom of said fins, wherein all of said refrigerant which enters said fourth portion of serpentine pipe, said fifth portion of serpentine pipe, and said sixth portion of serpentine pipe exits through said sixth primary exit pipe; and said third module's said ninth portion of serpentine pipe has a ninth primary exit pipe connected to a third vertically oriented pipe, said ninth primary exit pipe is connected to said third vertically oriented pipe outside of said length of fins and to the right of said rightmost fin and at a point about at about said bottom of said fins, wherein all of said refrigerant which enters said seventh portion of serpentine pipe, said eighth portion of serpentine pipe, and said ninth portion of serpentine pipe exits through said ninth primary exit pipe; and said third primary exit pipe, said sixth primary exit pipe and said ninth primary exit pipe are all connected to a primary exit manifold, said primary exit manifold having only a single exit, which all said refrigerant exits.
 13. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 12 wherein said refrigerant which exits through said primary exit manifold flows to a compressor, which compresses said refrigerant, exiting the compressor by a compressor pipe.
 14. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 13 including a pump connected to said compressor pipe to cause said refrigerant to flow into said refrigerant input manifold where said refrigerant continues to flow through a first module input pipe into said first module, a second module input pipe into said second module and a third module input pipe into said third module.
 15. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 1 wherein said programmable computer may be selected from the group consisting of a microprocessor, microprocessors, a MM/10 device (Multi-Input, Multi-Output Controller) and numerical control devices.
 16. A refrigerant flow control apparatus for an evaporative atmospheric water condenser as claimed in claim 8 wherein said programmable computer may be selected from the group consisting of a microprocessor, microprocessors, a MIMO device (Multi-Input, Multi-Output Controller) and numerical control devices. 